air source heat pump

Abstract

This application discloses an air source heat pump, including a compressor, an evaporator, a gas cooler, a phase change heat storage device, a fluid drive component, and a switching assembly. A first refrigerant channel of the gas cooler and a second refrigerant channel of the phase change heat storage device are connected in parallel to the compressor exhaust side; a first heat transfer fluid channel of the gas cooler and a second heat transfer fluid channel of the phase change heat storage device are connected in parallel; the switching assembly controls the selective flow of each channel. Through the cooperation of parallel flow paths and the switching assembly, this application can flexibly switch between multiple operating modes, such as heat storage only, heat release only, and combined heating, solving the problems of rigid modes and poor energy distribution flexibility in related technologies, and improving the system's adaptability to different load demands and operating scenarios.

Description

Technical Field

[0001] This application relates to the field of air source heat pump technology. More specifically, it relates to an air source heat pump. Background Technology

[0002] Air source heat pump systems face the dual challenges of operating costs and load adaptability in actual operation. (Transcritical) Air source heat pumps rely on The unique temperature glide characteristics of the working fluid during the supercritical heat release process can be well matched with the temperature rise process of water, reducing irreversible heat exchange losses. Therefore, it has attracted widespread attention in the fields of domestic hot water production and heating.

[0003] In related technologies, the refrigerant circuit and water-side circuit of air source heat pumps are both connected in series in a fixed manner—in the energy storage mode, the refrigerant must flow through all heat storage components in sequence, and in the heating mode, the water source must also flow through each heat exchange component in sequence.

[0004] The above-mentioned technical solutions result in the system being unable to flexibly switch to different operating modes such as "direct heating only", "heat release only" or "selective heat storage" according to heat load demand, changes in ambient temperature and differences in operating costs at different times. This leads to technical problems such as rigid operating modes and poor energy distribution flexibility. Summary of the Invention

[0005] This application provides an air source heat pump that connects the first refrigerant channel of a gas cooler and the second refrigerant channel of a phase change heat storage device in parallel to the compressor exhaust side, and connects the first heat transfer fluid channel of the gas cooler and the second heat transfer fluid channel of the phase change heat storage device in parallel. By controlling the selective flow of each channel through a switching component, it achieves integrated multi-mode heating such as pure heat storage, pure heat release, and combined heating.

[0006] This application provides an air source heat pump comprising a compressor, an evaporator, a gas cooler, a phase change heat storage device, a fluid drive component, and a switching assembly, wherein:

[0007] The evaporator is connected to the suction end of the compressor; the gas cooler is connected to the discharge end of the compressor, and the gas cooler includes a first refrigerant passage and a first heat transfer fluid passage connected to the discharge end of the compressor; the phase change heat storage device includes a phase change material layer, a second refrigerant passage and a second heat transfer fluid passage; the second refrigerant passage is connected in parallel with the first refrigerant passage; the second heat transfer fluid passage and the second refrigerant passage exchange heat through the phase change material layer, and the second heat transfer fluid passage and the first heat transfer fluid passage are connected in parallel; a fluid drive component is disposed on the parallel inlet side of the second heat transfer fluid passage and the first heat transfer fluid passage; a switching assembly is used to control the selective flow of the first refrigerant passage, the first heat transfer fluid passage, the second refrigerant passage and the second heat transfer fluid passage.

[0008] In the above technical solution, the first refrigerant channel of the gas cooler and the second refrigerant channel of the phase change heat storage device are connected in parallel to the exhaust side of the compressor. Simultaneously, the first heat transfer fluid channel of the gas cooler and the second heat transfer fluid channel of the phase change heat storage device are connected in parallel to the heat transfer fluid circuit. A switching assembly is installed to selectively control the on / off state of each channel, allowing the system to flexibly switch the flow paths of the refrigerant and heat transfer fluid according to actual operating requirements. Compared to the series fixed flow path of existing technologies, this solution can achieve multiple operating modes such as "only the gas cooler operates," "only the phase change heat storage device operates," "both operate simultaneously," and "independent heat storage / release," thereby significantly improving the flexibility of energy distribution and solving the problem of rigid operating modes.

[0009] In some embodiments, the phase change heat storage device includes a shell, a finned tube heat exchange core disposed within the shell, and a phase change material layer. The finned tube heat exchange core includes a second refrigerant channel and a second heat transfer fluid channel. The refrigerant and the heat transfer fluid exchange heat with the phase change material layer through their respective tube walls. The phase change material layer fills the space between the second refrigerant channel, the second heat transfer fluid channel, and the shell.

[0010] This technical solution involves filling the space between the outer shell and the finned tube heat exchange core with a phase change material layer, creating a tight contact between the phase change material and the finned tube, thus greatly increasing the heat exchange contact area. The finned tube heat exchange core integrates a second refrigerant channel and a second heat transfer fluid channel, which are independent of each other and both exchange heat with the same phase change material layer.

[0011] When the refrigerant flows through the second refrigerant channel, heat is efficiently transferred to the phase change material layer through the pipe wall and fins, causing the phase change material to melt and store heat; when the heat transfer fluid flows through the second heat transfer fluid channel, heat is transferred from the phase change material layer through the fins and pipe wall to the heat transfer fluid, thus releasing heat.

[0012] Because the finned tube structure significantly expands the heat exchange surface and the phase change material is completely filled in the fin gaps and inside the shell, the entire phase change material layer can participate in the phase change process uniformly, avoiding local overheating or insufficient heat storage.

[0013] Furthermore, the outer shell serves a sealing and shaping function, effectively preventing leakage of the phase change material and improving long-term operational stability. Compared to heat storage structures with only smooth pipes, this solution significantly improves the heat storage / release rate and energy density, resulting in faster response and a more compact structure.

[0014] In some embodiments, the air source heat pump further includes:

[0015] The controller is electrically connected to the switching assembly;

[0016] The controller is configured to, when the air source heat pump is in the first mode, switch the switching components to open the second refrigerant passage and close the first refrigerant passage, the second heat transfer fluid passage, and the first heat transfer fluid passage, so that the refrigerant flows only through the second refrigerant passage.

[0017] In the first mode, the refrigerant passes through the second refrigerant channel of the phase change heat storage device without passing through the gas cooler, and the heat transfer fluid side is completely closed. Therefore, all the heat output by the compressor is absorbed and stored by the phase change material layer, achieving pure "heat storage operation".

[0018] This mode is suitable for periods of low electricity prices or low system load conditions. It can efficiently convert electrical energy into latent heat of phase change and store it to provide a heat source for subsequent peak heating periods, thereby achieving economical operation.

[0019] Meanwhile, since the first refrigerant channel is closed, the refrigerant will not lose heat to the gas cooler, and the heat storage efficiency is significantly improved.

[0020] In some embodiments, the air source heat pump further includes:

[0021] The controller is electrically connected to the switching assembly;

[0022] The controller is configured to, when the air source heat pump is in the second mode, switch the switching components to open the second heat transfer fluid channel, close the first heat transfer fluid channel and the second refrigerant channel, and control the compressor to stop, and use the phase change heat storage device to exchange heat with the heat transfer fluid.

[0023] In the second mode, the compressor is stopped, refrigerant circulation ceases, and the switching assembly only opens the second heat transfer fluid channel while closing the first heat transfer fluid channel and the second refrigerant channel. The fluid drive component drives the heat transfer fluid through the second heat transfer fluid channel of the phase change heat storage device, absorbing previously stored heat from the phase change material layer through heat exchange and delivering the heat to the user end.

[0024] This mode enables "purely exothermic" operation, meaning it consumes no electrical energy from the compressor and relies solely on the latent heat stored in the phase change heat storage device to meet the heat load demand. This is particularly advantageous during peak electricity price periods or in scenarios requiring energy conservation, significantly reducing operating costs.

[0025] In some embodiments, the air source heat pump further includes:

[0026] The controller is electrically connected to the switching assembly;

[0027] The controller is configured to start the compressor to circulate the refrigerant when the air source heat pump is in the third mode, open the second heat transfer fluid channel and the first heat transfer fluid channel, close the second refrigerant channel, and exchange heat with the heat transfer fluid using the phase change heat storage device and the gas cooler.

[0028] In the third mode, the compressor starts and the refrigerant circulation proceeds normally, but the refrigerant only flows through the first refrigerant channel of the gas cooler and not through the second refrigerant channel of the phase change heat storage device; at the same time, the heat transfer fluid flows through both the first heat transfer fluid channel of the gas cooler and the second heat transfer fluid channel of the phase change heat storage device.

[0029] At this point, the heat transfer fluid absorbs the heat generated by the refrigerant in real time at the gas cooler and absorbs the heat stored in the phase change material layer at the phase change heat storage device, forming a combined heating mode of "instant heating from the gas cooler + supplementary heating from the phase change heat storage device". This mode is suitable for peak heat loads or situations where the phase change heat storage device has insufficient heat. It can quickly increase the outlet water temperature or increase the heat supply to ensure thermal comfort at the user end, while making full use of the residual heat in the heat storage device to avoid energy waste.

[0030] In some embodiments, the switching assembly includes a first valve, a second valve, a third valve, and a fourth valve, wherein the first valve is located at the outlet end of the second heat transfer fluid channel; the second valve is located between the inlet end of the first refrigerant channel and the inlet end of the second refrigerant channel; the third valve is located between the outlet end of the first refrigerant channel and the inlet of the evaporator; and the fourth valve is located at the outlet of the fluid drive component and the inlet side of the first heat transfer fluid channel.

[0031] This technical solution specifically defines the installation positions of four valves, forming an independent control capability for two refrigerant channels and two heat transfer fluid channels. The second valve is positioned between the inlet ends of the two parallel refrigerant channels, allowing the first refrigerant channel to be opened or closed. The first and fourth valves control the outlet of the second heat transfer fluid channel and the inlet of the first heat transfer fluid channel, respectively. Combined with the third valve's control of the refrigerant circuit's on / off state, precise switching between the first, second, and third modes can be achieved with a minimum number of valves. This valve layout has a simple structure and clear control logic, which helps reduce manufacturing costs and improve system reliability.

[0032] In some embodiments, the air source heat pump further includes a first temperature detection component, a second temperature detection component, and a controller, wherein: the first temperature detection component is used to detect the outlet water temperature of the air source heat pump; the second temperature detection component is used to detect the phase change temperature of the phase change material layer; and the controller is electrically connected to the first temperature detection component, the second temperature detection component, a first valve, a second valve, a third valve, and a fourth valve.

[0033] The controller is configured to, when the electricity price is less than a preset price, the phase change temperature does not reach a first preset threshold, the water flow rate of the air source heat pump is equal to zero, or the difference between the water outlet temperature and the set temperature is less than a first preset difference, control the air source heat pump to enter a first mode, start the compressor, open the second valve, and close the first, third, and fourth valves.

[0034] This technical solution incorporates multi-temperature detection and electricity price judgment logic to achieve automatic entry control in the first mode. When the electricity price is low (usually during off-peak hours) and the system does not need to supply water, if the phase change heat storage device is not yet fully charged (the phase change temperature is below the set threshold), and the temperature difference between the inlet and outlet of the second heat transfer fluid channel remains small (indicating that the current heat load at the user end is not large and the system does not need to provide a large amount of heat immediately), the controller will automatically switch to the first mode for heat storage.

[0035] This control logic can intelligently identify favorable energy storage opportunities, avoiding blind heat storage during periods of high electricity prices or high heat loads. This allows for maximum utilization of low-priced electricity while ensuring users' heating needs are met, thus reducing overall operating costs. Furthermore, the determination of the duration of the temperature difference prevents erroneous mode switching caused by instantaneous fluctuations, improving control stability.

[0036] In some embodiments, the controller is configured to control the air source heat pump to enter a second mode, open the first valve, and close the second, third, and fourth valves when the electricity price is greater than a preset price, the water flow rate of the air source heat pump is greater than zero, the difference between the water temperature and the set temperature is greater than a second preset difference, and the phase change temperature is greater than a second preset threshold.

[0037] This technical solution establishes automatic entry conditions for the second mode (pure heat release). When electricity prices are high (typically during peak hours) and the system needs to supply water, if the user-side heat load is large (manifested as a sustained large temperature difference between the inlet and outlet of the second heat transfer fluid channel), and the phase change thermal storage device has stored sufficient heat (phase change temperature exceeding a set threshold), the controller switches to the second mode, the compressor stops, and the system relies solely on the phase change thermal storage device to release heat to meet user needs. This control method fully utilizes the low-cost thermal energy stored during off-peak electricity prices, replacing compressor energy consumption during peak electricity price periods, significantly saving operating electricity costs. Simultaneously, by continuously judging the temperature difference threshold and time, it ensures that the pure heat release mode is only entered when there is sufficient heat storage and a genuine heating demand, avoiding the improper use of thermal storage resources.

[0038] In some embodiments, the controller is configured to operate when the outlet water flow rate of the air source heat pump is greater than zero and the difference between the outlet water temperature and the set temperature is greater than a second preset difference, or when the outlet water flow rate of the air source heat pump is greater than zero and the difference between the phase change temperature and the second preset threshold is less than a third preset difference.

[0039] Control the air source heat pump to enter the third mode, turn on the compressor, open the first valve, the third valve and the fourth valve, and close the second valve.

[0040] This technical solution sets entry conditions for the third mode (combined heating): On the one hand, when the user-side heat load is too high (the temperature difference between the inlet and outlet remains large), even if the electricity price may be high, the system will activate the third mode, simultaneously using the gas cooler for immediate heating and the phase change thermal storage device for heat release to ensure sufficient heating capacity; on the other hand, when the heat of the phase change thermal storage device is about to be exhausted (the difference between the phase change temperature and the threshold is less than the third preset difference), the system automatically enters the third mode, using the gas cooler to supplement heating and prevent the outlet water temperature from dropping. This control strategy achieves a balance between economic efficiency and heating reliability: it prioritizes the use of thermal storage devices to save electricity costs, while promptly activating the compressor to ensure heating when thermal storage is insufficient or demand is urgent, improving the system's adaptability under all operating conditions and user comfort.

[0041] In some embodiments, the controller is configured to control the first valve and the fourth valve to alternately open and close according to a preset duty cycle when the air source heat pump is in the third mode.

[0042] In the third mode (combined heating), the first valve controls the heat release flow rate of the second heat transfer fluid channel of the phase change thermal storage device, and the fourth valve controls the instantaneous hot water supply flow rate of the first heat transfer fluid channel of the gas cooler. By alternately opening and closing these two valves according to a preset duty cycle, the heat supply ratio between the phase change thermal storage device and the gas cooler can be adjusted, achieving precise temperature control and energy management. For example, when the outlet water temperature is too high, the duty cycle can be reduced to decrease the flow rate on the gas cooler side; when the phase change thermal storage device has sufficient heat, the opening time of the first valve can be extended to prioritize the use of stored heat. Periodic alternating control can also avoid local overheating or overcooling caused by long-term stagnation of a certain loop, balance the thermal stress of various components in the system, and extend the equipment life. This control method has a simple structure, rapid response, and can achieve continuous heating regulation without the need for additional regulating valves.

[0043] The air source heat pump proposed in this application includes a compressor, an evaporator, a gas cooler, a phase change heat storage device, a fluid drive component, and a switching assembly. The first refrigerant channel of the gas cooler and the second refrigerant channel of the phase change heat storage device are connected in parallel to the compressor exhaust side; the first heat transfer fluid channel of the gas cooler and the second heat transfer fluid channel of the phase change heat storage device are connected in parallel; the switching assembly controls the selective flow of each channel. Through the cooperation of parallel flow paths and the switching assembly, this application can flexibly switch between multiple operating modes, such as heat storage only, heat release only, and combined heating, solving the problems of rigid modes and poor energy distribution flexibility in related technologies, and improving the system's adaptability to different load demands and operating scenarios. Attached Figure Description

[0044] To more clearly illustrate the implementation methods in the embodiments of this application or related technologies, the accompanying drawings used in the description of the embodiments or related technologies will be briefly introduced below. Obviously, the accompanying drawings described below are some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings.

[0045] Figure 1 This is a schematic diagram of the system structure of the air source heat pump proposed in this application;

[0046] Figure 2 This is a schematic diagram of the phase change heat storage device proposed in this application;

[0047] Figure 3 This is a cross-sectional view of the phase change thermal storage device proposed in this application;

[0048] Figure 4 This is a schematic diagram of the refrigerant circuit proposed in this application;

[0049] Figure 5 This is a schematic diagram of the heat transfer fluid circuit proposed in this application;

[0050] Figure 6 This is an electrical connection block diagram of the controller and switch assembly proposed in this application;

[0051] Figure 7 This is a schematic diagram of the system flow of refrigerant and heat transfer fluid in the first mode of the air source heat pump proposed in this application.

[0052] Figure 8 This is a schematic diagram of the system flow direction of the refrigerant and heat transfer fluid in the second mode of the air source heat pump proposed in this application.

[0053] Figure 9 This is a schematic diagram of the system flow of refrigerant and heat transfer fluid in the third mode of the air source heat pump proposed in this application.

[0054] Figure 10 This is a schematic diagram of the valve arrangement and pipeline connection of the switch assembly proposed in this application;

[0055] Figure 11 This is an electrical connection block diagram of the controller and temperature sensing component proposed in this application;

[0056] Figure 12 This is a schematic diagram showing the valve flow direction of the refrigerant and heat transfer fluid in the first mode of the air source heat pump proposed in this application.

[0057] Figure 13 This application presents a schematic diagram of the valve flow direction of the refrigerant and heat transfer fluid in the second mode of the air source heat pump;

[0058] Figure 14 This is a schematic diagram showing the valve flow direction of the refrigerant and heat transfer fluid in the third mode of the air source heat pump proposed in this application.

[0059] Figure 15 This is a schematic flowchart of the control method for the air source heat pump proposed in this application.

[0060] Explanation of reference numerals in the attached figures:

[0061] 1-Compressor; 2-Evaporator; 3-Gas cooler;

[0062] 4-Phase change thermal storage device; 5-Throttling device; 6-Fluid drive component; 7-Switching assembly;

[0063] 71-First valve; 72-Second valve; 73-Third valve; 74-Fourth valve;

[0064] 31-First refrigerant channel; 32-First heat transfer fluid channel; 43-Phase change material layer;

[0065] 42-Finned tube heat exchanger core; 421-Second refrigerant channel; 422-Second heat transfer fluid channel;

[0066] 4211 - First inlet; 4212 - First outlet; 4221 - Second inlet; 4222 - Second outlet;

[0067] 41-Housing; 8-Controller; 91-First temperature detection component; 92-Second temperature detection component. Detailed Implementation

[0068] To make the objectives, implementation methods and advantages of this application clearer, the exemplary implementation methods of this application will be clearly and completely described below with reference to the accompanying drawings of the exemplary embodiments of this application. Obviously, the described exemplary embodiments are only some embodiments of this application, and not all embodiments.

[0069] It should be noted that the brief descriptions of terms in this application are only for the convenience of understanding the embodiments described below, and are not intended to limit the embodiments of this application. Unless otherwise stated, these terms should be understood in their ordinary and common meaning.

[0070] Furthermore, the terms “comprising” and “having”, and any variations thereof, are intended to cover but not exclusively include, for example, a product or device that includes a series of components is not necessarily limited to those that are explicitly listed, but may include other components that are not explicitly listed or that are inherent to such product or device.

[0071] Air source heat pumps, as a highly efficient and clean heating technology, have been widely used in building heating and domestic hot water preparation. Among them, transcritical carbon dioxide (CO2) Heat pumps use natural media as the circulating medium, which has the environmentally friendly advantages of ODP (Ozone Depletion Potential) = 0 and GWP (Global Warming Potential) = 1. At the same time, its gas cooler side has a large temperature glide, which can achieve good temperature matching with the heated medium such as water. Therefore, it has high energy efficiency potential and application value in the field of high-temperature hot water preparation.

[0072] However, existing transcritical Heat pump systems still face several technical bottlenecks in engineering applications and energy management scenarios. First, user-side heat loads exhibit significant time-varying and peak-valley fluctuations, while the efficient and stable operation of air-source heat pump units typically relies on relatively stable operating conditions. When the load changes rapidly, supply and demand mismatches can easily occur, leading to frequent start-ups and shutdowns or significant adjustments of the unit, thereby reducing the overall energy efficiency of the system and accelerating the wear and tear of key components such as the compressor.

[0073] Secondly, under the time-of-use pricing system, if the system lacks efficient and large-capacity thermal storage devices, it will be difficult to store heat during low-price periods and release it during high-price periods to cover the load. It will often be forced to maintain a high load during peak periods, which will not only increase operating costs but also increase the pressure on the grid peak load, making it difficult to achieve flexible control of thermal power load.

[0074] Third, although phase change thermal storage has advantages such as high energy density and stable phase change temperature, commonly used phase change materials have low thermal conductivity, making it difficult to match their heat transfer capacity with the charge and release rates across critical conditions. High-pressure side heat flux density and rapid heat exchange requirements can easily lead to problems such as delayed heat storage / release response and increased temperature difference at the heat exchange end, thus limiting the system's energy efficiency improvement and stable operation under dynamic conditions.

[0075] In related technologies, in order to improve the supply and demand matching problem under the fluctuation of user-side heat load, gas coolers and heat storage devices are connected in series. However, the flow path is fixed, and it is difficult to achieve flexible switching between independent heat storage, independent heating and combined heating modes through parallel valve groups. This is not conducive to fine scheduling and control. Moreover, the series arrangement results in long pipelines and large flow resistance, which increases pump power loss and makes it difficult to balance compactness, cost and energy efficiency requirements.

[0076] Based on the above, this application provides an air source heat pump that connects the first refrigerant channel of a gas cooler and the second refrigerant channel of a phase change heat storage device in parallel to the compressor exhaust side, and connects the first heat transfer fluid channel of the gas cooler and the second heat transfer fluid channel of the phase change heat storage device in parallel. Selective flow in each channel is controlled by a switching assembly, achieving integrated operation of multiple modes such as pure heat storage, pure heat release, and combined heating. By introducing a parallel flow path structure and automatic switching by the controller, the limitation of series fixed flow paths on mode flexibility is eliminated. The synergistic effect of these structures automatically completes intelligent switching between multiple modes without manual intervention, thereby solving the technical problems of rigid operating modes and poor energy distribution flexibility, and improving the system's adaptability to variable load and variable electricity price conditions.

[0077] The technical solutions of this application will be described in detail below with reference to specific embodiments. The following specific embodiments can be combined with each other or exist independently. The same or similar concepts or processes may not be described again in some embodiments. The embodiments of this application will be described below with reference to the accompanying drawings.

[0078] Figure 1 This is a schematic diagram of the system structure of the air source heat pump proposed in this application, as shown below. Figure 1 As shown, the air source heat pump includes a compressor 1, an evaporator 2, a gas cooler 3, a phase change heat storage device 4, a fluid drive component 6, and a switching assembly 7.

[0079] Compressor 1 has an intake end and an exhaust end. The outlet of evaporator 2 is connected to the intake end of compressor 1.

[0080] The gas cooler 3 includes a first refrigerant passage 31 and a first heat transfer fluid passage 32. The inlet end of the first refrigerant passage 31 is connected to the exhaust end of the compressor 1, and the outlet end of the first refrigerant passage 31 is connected to the inlet of the evaporator 2. The first heat transfer fluid passage 32 has a first water inlet and a first water outlet for the flow of heat transfer fluid. In this embodiment, the heat transfer fluid is water.

[0081] like Figure 3 As shown, the phase change heat storage device 4 includes a phase change material layer 43. The phase change material layer 43 is composed of a phase change material with a high latent heat of phase change, and its phase change temperature is set according to the application scenario of the air source heat pump. The phase change material can be selected from organic phase change materials (such as paraffin wax, fatty acids), inorganic hydrated salts (such as... , (or one or more of its composite phase change materials).

[0082] To improve the inherent defect of low thermal conductivity of phase change materials, high thermal conductivity fillers, such as expanded graphite, carbon nanotubes, metal powder or foam metal skeleton, can be added to the phase change material layer 43 to form a composite phase change material, thereby significantly improving the heat storage / release rate.

[0083] The phase change heat storage device 4 also includes a second refrigerant channel 421. The second refrigerant channel 421 and the first refrigerant channel 31 are connected in parallel.

[0084] The parallel connection of the second refrigerant passage 421 and the first refrigerant passage 31 means that the first inlet end 4211 of the second refrigerant passage 421 is connected to the exhaust end of the compressor 1 and is connected in parallel with the inlet end of the first refrigerant passage 31 through a pipeline; the first outlet end 4212 of the second refrigerant passage 421 is connected to the inlet of the evaporator 2 and is connected in parallel with the outlet end of the first refrigerant passage 31.

[0085] The phase change heat storage device 4 also includes a second heat transfer fluid channel 422. The second heat transfer fluid channel 422 and the second refrigerant channel 421 exchange heat through the phase change material layer 43, and the second heat transfer fluid channel 422 and the first heat transfer fluid channel 32 are connected in parallel.

[0086] The parallel connection of the second heat transfer fluid channel 422 and the first heat transfer fluid channel 32 means that the second inlet end 4221 of the second heat transfer fluid channel 422 is connected to the outlet of the fluid drive component 6, and the second outlet end 4222 of the second heat transfer fluid channel 422 is used to connect to the user end; the first inlet of the first heat transfer fluid channel 32 is also connected to the outlet of the fluid drive component 6 in parallel; the first outlet is also connected to the user end.

[0087] The fluid drive component 6 is disposed on the parallel inlet side of the second heat transfer fluid channel 422 and the first heat transfer fluid channel 32, meaning its outlet end is simultaneously connected to the second inlet end 4221 of the second heat transfer fluid channel 422 and the first inlet of the first heat transfer fluid channel 32. The fluid drive component 6 drives the heat transfer fluid (typically water or a mixture of water and antifreeze) to circulate throughout the entire heat transfer fluid loop, providing circulation power for the heat transfer fluid. By controlling the start / stop and rotational speed of the fluid drive component 6, the flow rate and velocity of the heat transfer fluid can be adjusted to match the heating demand under different operating modes.

[0088] In some embodiments, the fluid drive component 6 can be configured as a circulating water pump. The circulating water pump can be a constant speed pump or a variable frequency pump.

[0089] When using a constant-speed pump, the flow of the heat transfer fluid is controlled by the valves in the switching assembly; when using a variable-frequency pump, the flow rate can be continuously changed by adjusting the pump speed, achieving more precise control of the heat output. To reduce energy consumption, circulating water pumps should preferably be high-efficiency canned motor pumps or pumps driven by permanent magnet synchronous motors.

[0090] In addition, the number of fluid drive components 6 is not limited to one; multiple pump sets can be set in parallel or in series according to the pipeline layout to achieve redundancy backup or regional circulation.

[0091] In some embodiments, the air source heat pump includes a throttling device 5, with the inlet of the evaporator 2 connected to the outlet of the throttling device 5.

[0092] The throttling device 5 is an electronic expansion valve. The electronic expansion valve's opening degree can be adjusted in real time by the controller 7 according to system operating parameters (such as compressor discharge temperature, suction superheat, high-pressure side pressure, etc.), thereby precisely controlling the refrigerant flow rate and evaporator liquid supply, improving the system's energy efficiency ratio and stability. The stepper motor drives the valve needle of the electronic expansion valve to move, achieving continuous adjustment of the opening degree from fully closed to fully open, with fast response speed and high control accuracy.

[0093] In other embodiments, the throttling device 5 may also employ passive throttling elements such as a thermostatic expansion valve, capillary tube, or orifice plate to reduce manufacturing costs. In transcritical... In the heat pump system, the throttling device 5 is preferably an electronic expansion valve to meet the independent control requirements of pressure and temperature on the high-pressure side.

[0094] The switching assembly 7 is used to control the selective flow of the first refrigerant channel 31, the second refrigerant channel 421, the first heat transfer fluid channel 32, and the second heat transfer fluid channel 422.

[0095] Specifically, the switching assembly 7 can control the flow of the second refrigerant channel 421 only to store heat in the phase change material layer 43 in the phase change heat storage device.

[0096] The switching assembly 7 can also control the flow of only the second heat transfer fluid channel 422, so as to use only the phase change material layer 43 in the phase change heat storage device to release heat to the water.

[0097] The switching assembly 7 can also control the flow of the first refrigerant channel 31, the first heat transfer fluid channel 32, and the second heat transfer fluid channel 422, and close the second refrigerant channel 421 to utilize the phase change heat storage device and the gas cooler for coordinated heating.

[0098] This embodiment achieves flexible switching between different operating conditions by setting up a parallel and decoupled circulation architecture on the high-pressure side of the compressor. Specifically, by using switching components to execute different combinations of actions, multiple operating modes of the air source heat pump can be switched, thereby allocating heat storage and heating functions as needed according to heat load conditions. The beneficial effects of this design include: First, mode switching is more flexible, enabling rapid conversion between modes such as "heat storage only," "heat release only," and "combined heating," effectively decoupling the heat storage process from the heating process and significantly improving the system's operational flexibility and load-following capability; Second, because the gas cooler and phase change heat storage device are arranged in parallel on the high-pressure side of the refrigerant, in conjunction with valve group switching, the system's flow resistance and pressure drop are effectively reduced, improving the dynamic response characteristics and outlet water temperature stability during mode switching; Third, it enhances adaptability to load fluctuations and time-of-use electricity pricing environments, improves peak shaving and valley filling capabilities, thereby reducing operating costs.

[0099] Figure 2 This is a schematic diagram of the phase change heat storage device. Figure 3 This is a cross-sectional view of a phase change thermal storage device, such as... Figure 2 , Figure 3 As shown, the phase change heat storage device 4 includes a housing 41. The housing 41 is used to support and enclose the main body of the heat storage device and to provide a structural foundation for the installation of various pipeline interfaces.

[0100] The phase change heat storage device 4 includes a finned tube heat exchange core 42 disposed inside the outer casing 41. The finned tube heat exchange core 42 includes a second refrigerant channel 421 and a second heat transfer fluid channel 422 that are independently disposed of with respect to each other.

[0101] Both are provided with an inlet end and an outlet end. The first inlet end 4211 and the first outlet end 4212 of the second refrigerant channel 421 pass through the outer shell 41 respectively, and the second inlet end 4221 and the second outlet end 4222 of the second heat transfer fluid channel 422 pass through the outer shell 41 respectively.

[0102] The phase change heat storage device 4 includes a phase change material layer 43 filled between the outer shell 41 and the finned tube heat exchange core 42.

[0103] The above structure forms a direct coupling heat transfer link between the refrigerant, phase change material, and heat transfer fluid. This heat transfer link is short, resulting in higher heat storage or release efficiency and response. The refrigerant flows in the second refrigerant channel 421, and the heat transfer fluid flows in the second heat transfer fluid channel 422. Both exchange heat with the phase change material layer 43 outside the pipe through their respective pipe walls and fins, thus forming a direct coupling heat transfer path with the phase change material layer 43 as the intermediate heat storage / release medium.

[0104] Compared with the traditional indirect heat storage path of "refrigerant-water-phase change material", this structure reduces intermediate heat transfer links and thermal resistance, and can store high-grade heat on the compressor exhaust side more directly, improve energy storage density and heating quality, and significantly improve the charging and discharging rate.

[0105] By employing enhanced thermal conductivity designs, such as deeply embedding finned tubes within the phase change material layer to expand the effective heat transfer area, the effective thermal conductivity and heat transfer area on the phase change material side are significantly improved, thereby achieving high heat storage / release power and rapid dynamic response capabilities. Simultaneously, the flow boundary of the high-pressure refrigerant is confined to small-diameter pipes and their connections, reducing the high-pressure volume and sealing interface size, effectively improving pressure resistance and sealing safety, and enhancing the strength, reliability, and safety margin of the seal.

[0106] like Figure 2 As shown, the second inlet end 4221 and the second outlet end 4222 of the second refrigerant channel 421 and the second heat transfer fluid channel 422 are arranged at the top of the entire phase change heat storage device 4 to facilitate pipeline connection and operating condition switching.

[0107] The refrigerant flows in the second refrigerant channel 421, and the heat transfer fluid flows in the second heat transfer fluid channel 422. The refrigerant and the heat transfer fluid exchange heat with the phase change material layer 43 outside the pipe through the pipe wall and fins of their respective pipes, thereby forming a heat transfer link with the phase change material layer 43 as the intermediate heat storage / release medium.

[0108] Under heat storage conditions, the high-temperature refrigerant enters the second refrigerant channel 421 and releases heat inside the pipe. The heat is transferred to the phase change material layer 43 through the pipe wall and fins, causing the phase change material to heat up and melt, thereby storing the heat in the phase change material in the form of latent heat.

[0109] Under exothermic conditions, the heat transfer fluid enters the second heat transfer fluid channel 422 and absorbs heat and rises in temperature inside the pipe. The phase change material layer 43 solidifies and releases heat. The released heat is transferred to the heat transfer fluid through the fins and pipe wall, so that the heat transfer fluid obtains a relatively stable heat output near the phase change temperature.

[0110] When there is a demand for combined heating or supplemental heating, if the heat release capacity of the phase change heat storage device 4 is insufficient to heat the hot water to the set temperature, the hot water can be split between the second heat transfer fluid channel 422 and the first heat transfer fluid channel 32. One part of the hot water flows through the phase change heat storage device to absorb heat and increase its temperature, while the other part of the hot water flows through the gas cooler to supplement the heating. The two water streams merge and mix to form the hot water output, so as to maintain the set water supply temperature and improve the heating stability.

[0111] Compared with traditional shell-and-tube phase change accumulators, this structure utilizes finned tubes to tightly couple with the phase change material, which can significantly increase the equivalent heat exchange area with the phase change material and reduce the equivalent thermal resistance on the phase change material side. This alleviates the problem of limited charge / discharge / heat power caused by the low thermal conductivity of the phase change material, and improves the heat storage / discharge rate and dynamic response performance.

[0112] Meanwhile, transcritical The refrigerant flows and is pressurized within the pipes, while the heat transfer fluid also flows in separate pipes. The two are isolated from each other and achieve indirect heat exchange through a phase change material; in transcritical... Under high-pressure conditions, this arrangement helps to limit the high-pressure boundary to small-diameter pipelines and their connections, reduce the high-pressure volume and sealing interface size, and improve the reliability and safety margin of strength and sealing.

[0113] By utilizing the high energy density and near-isothermal heat release characteristics of phase change materials, a relatively stable hot water output can be provided during peak water usage periods, which is beneficial to reducing the frequent start-stop and inefficient operation of compressors under fluctuating loads and partial loads.

[0114] Meanwhile, the high-grade heat from the compressor exhaust side can be preferentially introduced into the phase change heat storage device for time-shifted storage during periods of low demand or off-peak electricity. When the heat storage is insufficient or the heat demand surges, the gas cooler can be switched to directly or supplementarily heat the water side, which is conducive to peak shaving and valley filling of heat and electricity loads, improving the economic efficiency of system operation, and reducing peak electricity demand and operating costs.

[0115] In some embodiments, such as Figure 4 As shown, the compressor 1, evaporator 2, first refrigerant passage 31, second refrigerant passage 421, and throttling device constitute a refrigerant circuit. The first refrigerant passage 31 and the second refrigerant passage 421 are connected in parallel. Switching between the first refrigerant passage 31 and the second refrigerant passage 421 is achieved by opening and closing the second valve 72 and the third valve 73.

[0116] like Figure 5 As shown, the first heat transfer fluid channel 32, the second heat transfer fluid channel 422, and the fluid drive component 6 constitute a heat transfer fluid circuit. The first heat transfer fluid channel 32 and the second heat transfer fluid channel 422 are connected in parallel, and the switching or coordination between the first heat transfer fluid channel 32 and the second heat transfer fluid channel 422 is realized by opening and closing the first valve 71 and the fourth valve 74.

[0117] In some embodiments, such as Figure 6 As shown, the air source heat pump also includes a controller 8, which is electrically connected to the switching assembly 7.

[0118] The controller 8 is also electrically connected to the compressor 1, the fluid drive component 6, and each temperature sensor to coordinate the overall control logic of the air source heat pump.

[0119] Controller 8 is configured as follows: Figure 7 As shown, when the air source heat pump is in the first mode, the compressor 1 is turned on and the switching component 7 is switched on to open the second refrigerant channel 421 and close the first refrigerant channel 31, the second heat transfer fluid channel 422 and the first heat transfer fluid channel 32, so that the refrigerant flows only through the second refrigerant channel 421.

[0120] Figure 7 The black dashed arrows indicate the refrigerant flow path. The first mode described above is a heat storage mode, in which the high-temperature, high-pressure refrigerant discharged from compressor 1 is stored in a heat storage mode. The refrigerant first enters the second refrigerant channel 421 of the phase change heat storage device 4, exchanges heat with the phase change material, and stores the heat in the phase change material in the form of latent heat.

[0121] The second heat transfer fluid channel 422 can be selected to stop the fluid drive component 6 and close the first valve 71 and the fourth valve 74 according to the water demand, so that the heat transfer fluid side does not participate in heat exchange; or, if a small amount of heat supply / maintaining loop circulation is required at the same time, the water side can be circulated at a set flow rate through the corresponding valve group.

[0122] In some implementations, the fluid drive component 6 is stopped to improve heat storage efficiency and reduce ineffective circulation losses.

[0123] In some embodiments, such as Figure 8 As shown, the controller 8 is configured to, when the air source heat pump is in the second mode, switch the switch assembly 7 to open the second heat transfer fluid channel 422, close the first heat transfer fluid channel 32 and the second refrigerant channel 421, and control the compressor 1 to stop, and use the phase change heat storage device to exchange heat with the heat transfer fluid.

[0124] Figure 8 The red dashed arrow in the middle indicates the flow path of the heat transfer fluid. The second mode mentioned above is the heat release mode. In this mode, the fluid drive component 6 is turned on, and cold water flows through the water-side heat exchange channel (second heat transfer fluid channel 422) of the phase change heat storage device under the drive of the fluid drive component 6. It absorbs the latent heat of phase change released by the phase change material and is heated before being output as domestic hot water.

[0125] In some embodiments, such as Figure 9 As shown, when the air source heat pump is in the third mode, the compressor 1 is started to circulate the refrigerant, the first refrigerant channel 31, the second heat transfer fluid channel 422 and the first heat transfer fluid channel 32 are opened, the second refrigerant channel 421 is closed, and the phase change heat storage device 4 and the gas cooler 3 are used to exchange heat with the heat transfer fluid.

[0126] Figure 9 The black dashed arrows indicate the refrigerant flow path, and the red dashed arrows indicate the heat transfer fluid flow path. The third mode described above is a synergistic heat release mode. In this mode, the heat transfer fluid is diverted in parallel between the second heat transfer fluid channel 422 and the first heat transfer fluid channel 32, and after mixing at the confluence point, it is output as hot water. On the refrigerant side, the high-pressure side of the refrigerant flows through the first refrigerant channel 31, and the compressor 1 starts, transcritical... The first refrigerant channel 31 is used to supplement the heating of the first heat transfer fluid channel 32 at the gas cooler, thereby stably meeting the outlet water temperature and flow requirements through the mixed heating method of "heat release from phase change heat storage device + heat supplementation from gas cooler".

[0127] like Figure 10 As shown, the switch assembly 7 includes a first valve 71, a second valve 72, a third valve 73, and a fourth valve 74.

[0128] The system comprises the following valves: a first valve 71 located between the outlet of the second heat transfer fluid channel 422 and the water supply end; a second valve 72 located at the parallel node between the inlet of the first refrigerant channel 31 and the first inlet 4211 of the second refrigerant channel 421, used to selectively open or close the second refrigerant channel 421; a third valve 73 located between the outlet of the first refrigerant channel 31 and the inlet of the throttling device 5; and a fourth valve 74 located between the outlet of the fluid drive component 6 and the first inlet of the first heat transfer fluid channel 32. The selective flow or switching of refrigerant between the first and second refrigerant channels 31 and 421 is achieved through the opening and closing states of the second valve 72 and the third valve 73. The second valve 72 and the third valve 73 are interlocked and mutually exclusive to prevent accidental opening in parallel, which could lead to an unintended connection between the high and low pressure sides of the refrigerant bypass circuit.

[0129] By controlling the opening and closing states of the first valve 71 and the fourth valve 74, the switching and coordinated heat exchange of the heat transfer fluid between the first heat transfer fluid channel 32 and the second heat transfer fluid channel 422 can be achieved.

[0130] This embodiment also enhances heat conduction and interlocking sequence control through finned tubes, making the system more stable, safer, and more economical. Specifically, the finned tubes are deeply embedded in the phase change material layer to increase the equivalent heat exchange area, improving the power limitation and temperature fluctuation problems caused by insufficient heat conduction on the phase change material side. At the same time, through valve interlocking and mutual exclusion, sequential switching, and hysteresis criteria combined with electricity price, load, and heat storage status, collaborative optimization scheduling is achieved, reducing the risk of frequent compressor start-stop and misconnection, thereby improving system stability, energy efficiency, and operating economy.

[0131] What we can know is that Figure 10The diagram shows only one configuration of the switch component 7. Those skilled in the art can select other valve combinations as needed, as long as they can satisfy the switching between channels.

[0132] Air source heat pumps include multiple temperature sensing components, such as Figure 11 As shown, two temperature detection components are provided, namely the first temperature detection component 91 and the second temperature detection component 92.

[0133] It should be noted that those skilled in the art can set up a corresponding number of temperature detection components as needed and use them to detect the required locations.

[0134] The first temperature detection component 91 is used to detect the outlet water temperature of the air source heat pump. The first temperature detection component 91 can be installed on the water inlet pipe at the water-using end.

[0135] The second temperature detection component 92 is used to detect the temperature of the phase change material layer 43. The second temperature detection component 92 can be embedded in the interior or surface of the phase change material layer 43.

[0136] The controller 8 is electrically connected to the first temperature detection component 91 and the second temperature detection component 92, respectively.

[0137] In some embodiments, such as Figure 12 As shown, the controller 8 is configured to control the air source heat pump to enter the first mode, turn on the compressor, open the second valve 72, and close the first valve 71, the third valve 73 and the fourth valve 74 when the electricity price is less than the preset price, the phase change temperature does not reach the first preset threshold, and the air source heat pump is not in the water outlet state.

[0138] Figure 12 The black dashed arrows indicate the refrigerant flow path. The first mode described above is a heat storage mode; in this mode, the high-temperature refrigerant discharged from compressor 1 is kept at a high temperature. The refrigerant first enters the second refrigerant channel 421 of the phase change heat storage device 4, exchanges heat with the phase change material, and stores the heat in the phase change material in the form of latent heat.

[0139] In the above, when the electricity price is lower than the preset price, it is determined that the time is either a low-priority period or an economic priority period.

[0140] In this embodiment, whether the air source heat pump is in a water-discharging state is determined by whether the water discharge flow rate of the air source heat pump is zero. When the water discharge flow rate is equal to zero, it is determined that no water is being discharged; when the water discharge flow rate is greater than zero, it is determined that the air source heat pump is in a water-discharging state.

[0141] The first preset threshold is a parameter used to characterize the upper limit of the heat storage state of the phase change heat storage device 4.

[0142] In some embodiments, the controller 8 is configured to control the air source heat pump to enter a first mode, turn on the compressor, open the second valve 72, and close the first valve 71, the third valve 73, and the fourth valve 74 when the electricity price is less than a preset price, the phase change temperature does not reach a first preset threshold, and the difference between the outlet water temperature and the set temperature is less than a first preset difference.

[0143] To avoid unnecessary circulation and possible crossflow on the refrigerant side, in this mode, the second valve 72 and the third valve 73 are kept closed to isolate the parallel branch on the high-pressure side of the refrigerant (or to be kept in a closed state adapted to the shutdown condition).

[0144] In some embodiments, when the difference between the outlet water temperature and the set temperature is less than a first preset difference and continues for a first preset time, and the electricity price is less than a preset price, and the phase change temperature does not reach a first preset threshold, the air source heat pump is controlled to enter a first mode.

[0145] When the water flow rate of the air source heat pump is zero or the difference between the water temperature and the set temperature is less than the first preset difference for a first preset time, it is determined that the heating demand is low or the demand is released.

[0146] In some embodiments, such as Figure 13 As shown, the controller is configured to control the air source heat pump to enter the second mode when the electricity price is greater than the preset price, the water flow rate of the air source heat pump is greater than zero, the difference between the water temperature and the set temperature is greater than the second preset difference, and the phase change temperature is greater than the second preset threshold, thereby opening the first valve 71 and closing the second valve 72, the third valve 73 and the fourth valve 74.

[0147] Figure 13 The red dashed arrow in the middle indicates the flow path of the heat transfer fluid. The second mode mentioned above is the heat release mode. In this mode, the fluid drive component 6 is turned on, and cold water flows through the water-side heat exchange channel (second heat transfer fluid channel 422) of the phase change heat storage device under the drive of the fluid drive component 6. It absorbs the latent heat of phase change released by the phase change material and is heated before being output as domestic hot water.

[0148] The first preset difference is greater than the second preset difference.

[0149] If the electricity price is higher than the preset price, it is determined that the current period is peak time.

[0150] The aforementioned second preset threshold is used to characterize the lower limit parameter at which the phase change heat storage device 4 cannot release heat. When the phase change temperature is greater than the second preset threshold, it is determined that the phase change heat storage device has usable heat release capacity.

[0151] By setting a first preset threshold and a second preset threshold, switching between modes involving heat storage or heat release is allowed only when the corresponding threshold is reached, in order to avoid frequent switching near critical operating conditions.

[0152] When the outflow rate is greater than zero and the difference between the outflow temperature and the set temperature is greater than the second preset difference, it is determined that the heating demand is valid or the heating demand increases.

[0153] In some embodiments, when the electricity price is greater than a preset price, the water flow rate of the air source heat pump is greater than zero, the difference between the water outlet temperature and the set temperature is greater than a second preset difference for a second preset time, and the phase change temperature is greater than a second preset threshold, the air source heat pump is controlled to enter a second mode, the first valve 71 is opened, and the second valve 72, the third valve 73 and the fourth valve 74 are closed.

[0154] In some embodiments, when the execution strategy of the air source heat pump requires reducing the compressor running time, and the heat demand is met, and the phase change temperature is greater than a second preset threshold, the control enters the second mode.

[0155] In some embodiments, such as Figure 14 As shown, the controller is configured to operate when the water flow rate of the air source heat pump is greater than zero and the difference between the water temperature and the set outlet temperature is greater than a second preset difference.

[0156] Alternatively, if the water flow rate of the air source heat pump is greater than zero and the difference between the phase change temperature and the second preset threshold is less than the third preset threshold, it is determined that the heat release capacity of the phase change heat storage device decreases and the heat release is insufficient.

[0157] To control the air source heat pump to enter the third mode, turn on the compressor, open the first valve 71, the third valve 73 and the fourth valve 74, close the second valve 72, and control the air source heat pump to enter the third mode. Figure 14 The black dashed arrows indicate the refrigerant flow path, and the red dashed arrows indicate the heat transfer fluid flow path. The third mode described above is a synergistic heat release mode. In this mode, the heat transfer fluid is diverted in parallel between the second heat transfer fluid channel 422 and the first heat transfer fluid channel 32, and after mixing at the confluence point, it is output as hot water. The third valve 73 on the refrigerant side opens, and the second valve 72 closes, allowing the high-pressure side of the refrigerant to flow through the first refrigerant channel 31. The compressor 1 starts, and the transcritical... The first refrigerant channel 31 is used to supplement the heating of the first heat transfer fluid channel 32 at the gas cooler, thereby stably meeting the outlet water temperature and flow requirements through the mixed heating method of "heat release from phase change heat storage device + heat supplementation from gas cooler".

[0158] In some embodiments, the controller is configured such that when the water flow rate of the air source heat pump is greater than zero and the difference between the water temperature and the set outlet temperature lasts for a second preset time greater than a second preset difference;

[0159] To control the air source heat pump to enter the third mode, turn on the compressor, open the first valve 71, the third valve 73 and the fourth valve 74, close the second valve 72, and control the air source heat pump to enter the third mode.

[0160] In some embodiments, when the air source heat pump is in the third mode, the first valve 71 and the fourth valve 74 are controlled to open and close alternately according to a preset duty cycle. This achieves equivalent flow regulation of the two parallel branches, thereby distributing the phase change heat release and heat pump heat compensation as needed, reducing the instantaneous load on the heat pump while ensuring that the outlet water temperature meets the set temperature.

[0161] In some implementations, the first valve 71 and the fourth valve 74 are periodically opened and closed.

[0162] In some embodiments, to prevent valve switching from causing misconnection of the flow path, resulting in unintended connection of the refrigerant bypass on the high and low pressure sides or unintended bypass of the water circuit, the controller adopts a valve interlocking and sequential switching strategy. Before switching to each mode, the compressor load is reduced or the compressor is briefly stopped. The sequential action of "closing the valves related to the current mode - delaying until the pressure difference / flow stabilizes - opening the valves related to the target mode" is executed first. After the valves are in place and the flow path is delayed until it stabilizes, the compressor operation is resumed.

[0163] In some embodiments, hysteresis is set for the difference between the outlet water temperature and the set temperature and the criteria for the phase change temperature. Mode switching is only allowed when the corresponding entry conditions are met and the preset delay conditions are continuously reached, so as to avoid frequent switching near the critical operating conditions.

[0164] like Figure 15 The diagram shown illustrates a flow chart of the control method for an air source heat pump in an embodiment of this application.

[0165] S1. The controller collects the setpoint Tset of the outlet water temperature, the actual outlet water temperature Tout, the outlet water flow rate Qw, the electricity price time period signal (valley period / normal period / peak period), and the phase change heat storage status signal.

[0166] Among them, the phase change heat storage state signal includes the phase change material temperature Tpcm.

[0167] In some embodiments, the phase change thermal storage status signal also includes the inlet and outlet temperature difference ΔTw of the second heat transfer fluid channel of the phase change thermal storage device, where ΔTw is defined as... Where Tw,out,pcm is the outlet of the second heat transfer fluid channel, and Tw,in,pcm is the inlet of the second heat transfer fluid channel. ΔTw is used to assist in determining the heat release or heat storage capacity of the phase change heat storage device.

[0168] The operating modes include at least: heat storage mode (first mode), heat release mode (second mode), phase change heat release-heat pump supplementary heat synergistic heating mode (third mode), and conventional heat pump heating mode (fourth mode).

[0169] S2. Calculate the difference between the outlet water temperature and the set temperature.

[0170] In this step, temperature deviation .

[0171] S3. Determine whether the difference is greater than the second preset difference for a second preset time and whether the outflow rate is greater than 0.

[0172] In step S3, if so, it is determined that there is a heat demand at this time, and step S4 is executed to determine whether the phase change temperature is greater than the second preset threshold.

[0173] In step S4, if so, it is determined that the phase change thermal storage device can provide heat at this time, and step S5 is executed to determine whether it is peak electricity consumption or whether a low compressor strategy is adopted.

[0174] If so in step S5, then proceed to step S6 to execute the second mode.

[0175] In this mode, the first valve is open, while the second, third, and fourth valves are closed, allowing domestic hot water to flow only through the second heat transfer fluid channel 422 to obtain phase change heat release. Simultaneously, the fourth valve is closed, preventing the water from flowing through the first heat transfer fluid channel 32. The compressor 1 is stopped or kept off-limits, and the phase change heat storage device 4 directly meets the outlet water temperature Tout's requirement for the setpoint Tset. This mode primarily utilizes stored heat for heating during periods of high electricity prices, reducing peak-hour electricity costs and decreasing compressor start-stop frequency. It is suitable for scenarios where peak water usage is concentrated and it is desirable to use heat storage to cover part of the peak load.

[0176] In some implementations, the controller can periodically open / close / control the duty cycle of the first valve to adjust the heat release intensity and stabilize Tout. When the phase change temperature is ≤ the second preset threshold or when ΔT is still greater than the first preset difference during the heat release and heating process and continues for more than the first preset time, the controller exits the mode and switches to the coordinated heating mode; when the off-peak period arrives and the heat demand is relieved, and the phase change temperature is < the first preset threshold, the controller can switch to the heat storage mode to continue heat storage.

[0177] If not in step S5, then proceed to step S7 to execute the third mode.

[0178] In this mode, the first, third, and fourth valves are opened, the second valve is closed, and the compressor is turned on, so that the water side is connected in parallel and split between the first heat transfer fluid channel 32 and the second heat transfer fluid channel 422. Part of the water flows through the phase change material layer 43 of the phase change heat storage device 4 to obtain heat release, and the other part of the water flows through the first refrigerant channel 31 of the gas cooler to obtain heat pump supplementary heat. The two paths merge downstream to form water outlet.

[0179] The third valve opens and the second valve closes, allowing the refrigerant to provide supplemental heat to the water side via the gas cooler without entering the second refrigerant channel 421 of the phase change heat storage device. The controller uses closed-loop regulation to adjust the compressor frequency and the opening of the electronic expansion valve to ensure stable outlet water temperature and flow rate to meet user requirements.

[0180] Simultaneously, the controller can periodically open / close / control the duty cycle of the first and fourth valves to achieve equivalent flow regulation of the two parallel branches, thereby distributing the phase change heat release and heat pump supplementation heat as needed, reducing the instantaneous load on the heat pump while ensuring that Tout meets Tset. The main function of this mode is to ensure heating stability under conditions such as high load, low inlet water temperature, or insufficient heat storage capacity, while still utilizing phase change heat release to reduce the instantaneous load on the heat pump; it is suitable for domestic hot water systems with high requirements for outlet water temperature stability, large load fluctuations, and inability to accept peak temperature drops.

[0181] Preferably, when Tout recovers to meet Tset and Tpcm > the second preset threshold and is in the peak period, the heat release mode can be switched back according to the electricity price and strategy; when the heat demand is relieved and is in the valley period, and Tpcm < the first preset threshold, the heat storage mode can be switched back to supplement the heat storage; when Tpcm ≤ the second preset threshold (heat storage is exhausted or the heat release capacity is insufficient), the controller can close the first valve and keep the third and fourth valves open, degenerating into the fourth mode where only the gas cooler provides heat.

[0182] To avoid frequent switching, a hysteresis threshold and a minimum holding time are set between the third mode and the first and second modes. During switching, an interlocking sequence of "unload / stop first - valve cut-in confirmation - delay stabilization - restart / lock stop" is executed to prevent refrigerant short circuit or water bypass caused by misconnection of flow path during valve switching.

[0183] If not in step S4, it is determined that the phase change thermal storage device is insufficient to provide heat, and step S8 is executed to execute the fourth mode. In this mode, only the gas cooler is used for heating, the fourth valve and the third valve are opened, the first valve and the second valve are closed, and the compressor is started.

[0184] In step S3, if not, it is determined that there is no heat demand at this time, and then step S9 is executed to determine whether the phase change temperature is less than the first preset threshold.

[0185] In step S9, if yes, then step S10 is executed to determine whether it is a non-peak electricity consumption period.

[0186] If so in step S10, then step S12 is executed to execute the first mode.

[0187] In this mode, the second valve is open, and the first, third, and fourth valves are closed, connecting the refrigerant circuit with the refrigerant heat exchange circuit of the phase change heat storage device to charge the phase change material, while simultaneously cutting off the heat exchange branch of the refrigerant through the gas cooler; under this valve position combination, both the first and fourth valves are closed, and the two parallel heat exchange branches on the water side do not participate in heat exchange.

[0188] The controller starts the compressor and adjusts the compressor frequency and electronic expansion valve opening according to a preset control strategy (e.g., aiming for optimal discharge pressure), thereby completing energy storage during periods of low electricity price / low load. The main function of this mode is to smooth out peak and valley loads, increase the utilization rate of low-priced electricity, and provide a heat storage margin for subsequent peak heating; it is suitable for domestic hot water systems with time-of-use pricing, fluctuating water loads, and the ability to pre-store heat during off-peak periods.

[0189] When the phase change temperature Tpcm ≥ the first preset threshold Tpcm, high (heat storage reaches the upper limit) or the heat demand is met / increased (Qw > 0 and ΔT ≥ the first preset difference ΔTon lasts for the first preset time) When the temperature drops, the system exits the current mode and switches to either heat release mode or coordinated heating mode based on electricity price and thermal storage availability, prioritizing ensuring that the outlet water temperature meets the set temperature Tset.

[0190] If not in step S10, then proceed to step S11.

[0191] If not in step S9, then proceed to step S11 to either standby or continuous monitoring.

[0192] This control method achieves mode discrimination and scheduling for heat storage / heat release / coordinated heating / conventional heat pump heating through multi-mode control based on time-of-use electricity pricing, load and heat storage status coordination, and valve group interlocking sequence switching strategy. Specifically, the controller determines whether the heating demand is established or canceled based on the first preset threshold, the second preset threshold, the first preset difference, and the second preset difference criterion, combined with water flow and duration. It adopts the interlocking and mutual exclusion configuration of the second and third valves, and the sequential switching of "unloading / stopping first - closing the valve - delaying stabilization - opening the valve - restarting" and the minimum duration constraint to avoid bypass misconnection and frequent switching, thereby improving system stability and economy. The air source heat pump proposed in this application constructs an enhanced heat exchange structure with direct coupling of three media: "refrigerant - phase change material - heat transfer fluid" to replace the multi-stage heat transfer path of traditional water-side indirect heat storage, thereby reducing intermediate thermal resistance and reducing the temperature difference required for heat exchange. At the same time, the thermal conductivity of the phase change material side is enhanced and the effective heat exchange area is increased through structural designs such as deep burial of finned tubes, so as to improve the heat storage / heat release power and thermal response rate. At the system level, a parallel and decoupled loop architecture on the high-pressure side is constructed based on a three-medium phase change heat storage device. Combined with a collaborative control strategy for multiple operating conditions, it enables on-demand switching and efficient and stable operation of modes such as "independent heat storage", "independent heat release" and "joint heating".

[0193] This embodiment achieves flexible switching between multiple operating modes, including pure heat storage, pure heat release, and combined heating, through parallel flow path design and selective control of switching components. This overcomes the limitations of existing series structures with their single-mode operation, improves the system's adaptability to varying loads and electricity prices, and reduces operating costs. The phase change heat storage device adopts a finned tube filled structure, resulting in high heat storage and release efficiency and a compact structure. Temperature detection and control logic ensures the accuracy and reliability of mode switching.

[0194] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this application, and are not intended to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features therein. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of this application.

[0195] For ease of explanation, the above description has been provided in conjunction with specific embodiments. However, the above exemplary discussion is not intended to be exhaustive or to limit the embodiments to the specific forms disclosed above. Various modifications and variations can be obtained based on the above teachings. The selection and description of the above embodiments are for the purpose of better explaining the principles and practical applications, thereby enabling those skilled in the art to better utilize the embodiments and various different variations of embodiments suitable for specific application considerations.

[0196] In this application, "and / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent three cases: A existing alone, A and B existing simultaneously, and B existing alone. Additionally, the character " / " in this document indicates that the preceding and following related objects have an "or" relationship.

[0197] "At least one of the following" or similar expressions refer to any combination of these items, including any combination of single or multiple items. For example, at least one of a, b, or c can mean: a, b, c, a and b, a and c, b and c, or a, b, and c, where each of a, b, and c can be an element itself or a set containing one or more elements.

[0198] In this application, "at least one" means one or more. "More than one" means two or more. The descriptions of "first," "second," etc., appearing in the embodiments of this application are only for illustration and to distinguish the described objects, and have no order, nor do they indicate a special limitation on the number of devices in the embodiments of this application, and cannot constitute any limitation on the embodiments of this application. For example, "first threshold" and "second threshold" are only used to distinguish different thresholds, and do not indicate that the size, priority, or importance of these two thresholds are different.

[0199] In this application, terms such as "exemplary," "in some embodiments," and "in other embodiments" are used to indicate that something is an example, illustration, or description. Any embodiment or design described as "exemplary" in this application should not be construed as being more preferred or advantageous than other embodiments or designs. Rather, the term "exemplary" is used to present the concept in a specific manner.

[0200] In this application, the terms "of", "corresponding", "corresponding", and "related" may sometimes be used interchangeably. It should be noted that when the distinction is not emphasized, they have the same meaning.

[0201] In this application, "equal to" can be used with "less than" or "greater than", but not simultaneously with both. When "equal to" is used with "less than", it applies to the technical solution adopted by "less than". When "equal to" is used with "greater than", it applies to the technical solution adopted by "greater than".

Claims

1. An air source heat pump, characterized in that, include: compressor; An evaporator is connected to the suction end of the compressor; A gas cooler, connected to the exhaust end of the compressor, the gas cooler comprising: The first refrigerant passage is connected to the discharge end of the compressor; First heat transfer fluid channel; Phase change heat storage device, the phase change heat storage device comprising: Phase change material layer; The second refrigerant channel is connected in parallel with the first refrigerant channel; The second heat transfer fluid channel and the second refrigerant channel exchange heat through the phase change material layer, and the second heat transfer fluid channel and the first heat transfer fluid channel are connected in parallel. A fluid drive component is disposed on the parallel inlet side of the second heat transfer fluid channel and the first heat transfer fluid channel; A switching assembly for controlling the selective flow of the first refrigerant channel, the first heat transfer fluid channel, the second refrigerant channel, and the second heat transfer fluid channel.

2. The air source heat pump according to claim 1, characterized in that, The phase change heat storage device includes: shell; A finned tube heat exchange core is disposed inside the outer shell; the finned tube heat exchange core includes a second refrigerant channel and a second heat transfer fluid channel, wherein the refrigerant and the heat transfer fluid exchange heat with the phase change material layer through their respective tube walls; The phase change material layer is filled between the second refrigerant channel, the second heat transfer fluid channel, and the outer casing.

3. The air source heat pump according to claim 1 or 2, characterized in that, Also includes: The controller is electrically connected to the switching assembly; The controller is configured to switch the switching assembly when the air source heat pump is in the first mode, to open the second refrigerant channel and close the first refrigerant channel, the second heat transfer fluid channel and the first heat transfer fluid channel, so that the refrigerant flows only through the second refrigerant channel.

4. The air source heat pump according to claim 1 or 2, characterized in that, Also includes: The controller is electrically connected to the switching assembly; The controller is configured to switch the switching assembly when the air source heat pump is in the second mode, to open the second heat transfer fluid channel, close the first heat transfer fluid channel and the second refrigerant channel, and control the compressor to stop, thereby utilizing the phase change heat storage device to exchange heat with the heat transfer fluid.

5. The air source heat pump according to claim 1 or 2, characterized in that, Also includes: The controller is electrically connected to the switching assembly; The controller is configured to, when the air source heat pump is in the third mode, start the compressor to circulate the refrigerant, open the first refrigerant channel, the second heat transfer fluid channel and the first heat transfer fluid channel, close the second refrigerant channel, and exchange heat with the heat transfer fluid using the phase change heat storage device and the gas cooler.

6. The air source heat pump according to claim 1 or 2, characterized in that, The switching assembly includes: The first valve is located at the outlet end of the second heat transfer fluid channel; The second valve is located between the inlet end of the first refrigerant passage and the inlet end of the second refrigerant passage; The third valve is located between the outlet end of the first refrigerant passage and the inlet of the evaporator; The fourth valve is located at the outlet of the fluid drive component and at the inlet of the first heat transfer fluid channel.

7. The air source heat pump according to claim 6, characterized in that, Also includes: The first temperature detection component is used to detect the outlet water temperature of the air source heat pump; The second temperature detection component is used to detect the phase transition temperature of the phase transition material layer; The controller is electrically connected to the first temperature detection component, the second temperature detection component, the first valve, the second valve, the third valve, and the fourth valve; The controller is configured to, when the electricity price is less than a preset price, the phase change temperature does not reach a first preset threshold, the water flow rate of the air source heat pump is equal to zero, or the difference between the water outlet temperature and the set temperature is less than a first preset difference, control the air source heat pump to enter a first mode, turn on the compressor, open the second valve, and close the first valve, the third valve, and the fourth valve.

8. The air source heat pump according to claim 7, characterized in that, The controller is configured to, when the electricity price is greater than a preset price, the water flow rate of the air source heat pump is greater than zero, the difference between the water outlet temperature and the set temperature is greater than a second preset difference, and the phase change temperature is greater than a second preset threshold, control the air source heat pump to enter a second mode, open the first valve, and close the second valve, the third valve, and the fourth valve.

9. The air source heat pump according to claim 8, characterized in that, The controller is configured such that when the outlet water flow rate of the air source heat pump is greater than zero and the difference between the outlet water temperature and the set temperature is greater than a second preset difference, Alternatively, when the water flow rate of the air source heat pump is greater than zero and the difference between the phase change temperature and the second preset threshold is less than the third preset difference; The air source heat pump is controlled to enter the third mode, the compressor is turned on, the first valve, the third valve and the fourth valve are opened, and the second valve is closed.

10. The air source heat pump according to claim 9, characterized in that, The controller is configured to control the first valve and the fourth valve to alternately open and close according to a preset duty cycle when the air source heat pump is in the third mode.

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